Pressure device



June 14, 1966 G; STURM 3,255,490

PRESSURE DEVICE Filed Oct. 22, 1964 2 Sheets-Sheet l INVENTOR.

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June 14, 1966 R. G. STURM 3,255,490

PRESSURE DEVICE Filed 001:. 22, 1964 2 Sheets-Sheet 2 United States Patent ce 3,255,490 PRESSURE DEVICE Rolland G. Sturm, 1320 Forbes Drive SE, Huntsville, Ala. Filed Oct. 22, 1964, Ser. No. 405,776 Claims. (Cl. 18--16) This invention relates in general to pressure generation. It deals more particularly with a device for generating ultra-high pressure.

A number of pressure devices are presently utilized for generating substantially high pressures to compact materials such as metal powders, for example, or compress other materials. These known devices are limited in the amount of pressure which they can practically generate, however. At present, maximum pressures of in the neighborhood of about 1,000,000 p.s.i. are considered feasible with devices of this type; one example being a tetrahedron arrangement of four anvils which nest together to exert pressure between them,

It is an object of the present invention to 'provide a new and improved device for generating ultra-high pressures.

It is another object to provide a device capable of generating pressures far in excess of 1,000,000 p.s.i.

It is still another object to provide an ultra-high pressure generating device wherein pressures are readily predictable throughout the operating range of the device.

It is yet another object to provide an ultra-high pressure generating device wherein material is subjected to substantially uniform pressure on all axes and minimal shear stresses are developed in the material.

It is a further object to provide an ultra-high pressure generating device incorporating a heating system for subjecting materials under pressure to substantially high temperatures.

It is still a further object to provide an ultra-high pressure generating device wherein the electrical conductivity of materials under pressure is readily tested.

The foregoing and other objects are realized in accord with the present invention by providing a device which is capable of developing and applying substantially uniform pressures in a range considerably higher than presently considered practicable. The pressure generating device embodies a series of concentric chambers in which increasingly higher pressures are developed and applied to material with minimal shear stress development in the material. Furthermore, the ultra-high pressure generating device is constructed so that even in the highest pressure generating range, far above 1,000,000 p.s.i., structural failure within the device is avoided.

The material being subjected to these pressures is readily subjected to relatively high temperatures, as desired. The electrical conductivity of the material under pressure is also readily determinable. In addition, a complete range of accurately predictable pressures are developed by the device in the series of concentric chambers, whereby the amount of compact-ion or compression is readily predictable.

The invention, both as to its organization and method of operation, taken with further objects and advantages thereof, will best be understood by reference to the following description taken in connection with the accompanying drawings, in which:

FIGURE 1 is a diagrammatic side elevational view of the ultra-high pressure generating device embodying features of the present invention;

FIGURE 2 is an enlarged sectional view taken along line 12-22 of FIGURE 1; and

FIGURE 3 is a further enlarged sectional view, with parts broken away, of a fluid seal construction employed in the pressure generating device.

3,255,490 Patented June 14, 1966 Referring now to the drawings, and particularly to FIGURE 1, a pressure generating device embodying features of the present invention is illustrated diagrammatically at 10. According to the present invention, the device 10 is capable of generating maximum pressures far in excess of 1,000,000 p.s.i. for effective application to the compaction or compression of material. The field of powder metallurgy is a good example of an art Where the device 10 finds ready application.

Actually, the ultra-high pressure device 10 illustrated is capable of generating pressures in the neighborhood of 1,500,000 p.s.i. to 2,500,000 p.s.i., and the invention lends itself to achieving even higher maximum pressures. This is in contrast to presently known pressure generating devices with which it has been found that maximum pres sures of only about 1,000,000 p.s.i. are feasible, as has been pointed out.

The ultra-high pressure generating device 10 includes a series of concentric chambers A, B, C, and D, in which increasingly greater pressures are generated from the I however, shear forces developed in the material being compressed or compacted are relatively low because of the uniformity of pressure application. Furthermore, the structural interior of the device 10 which is subjected to maximum pressures is constructed according to the pres ent invention to prevent failure under pressure,

In a manner which will hereinafter be discussed in detail, the pressures which can be achieved with the ultrahigh pressure generating device 10 are accurately predictable. Accordingly, a prescribed amount of compaction can be achieved in powder metallurgy, for example.

The construction of the ultra-high pressure generating device 10 further facilitates heating the chamber D to temperatures up to 2,000 F. Accordingly, materials being compacted or compressed can simultaneously be subjected to any desired temperature suitable for the operation in question. At the same time, the device 10 facilitates the testing of electrical conductivity of the material under pressure.

Referring to FIGURE 2, a detailed sectional view taken through one-quarter of the ultra-high pressure generating device 10 is illustrated. Since the device 10 is symmetrical, however, itwill be recognized that a description of this one-quarter section of the device will suffice to an understanding of the construction of the entire device.

The ultra-high pressure generating device 10 comprises three concentric pressure intensifying units 15, 16, and 17, nested within an outer cylinder 20. The pressure intensifying unit 15 is seated immediately within the cylinder 20 in spaced relationship therefrom whereby the continuous chamber A is defined between the unit and the cylinder. The chamber A is filled with a viscous liquid 22 which is, in the present instance, hydraulic fluid. The pressure intensifying unit 16 is seated immediately withinthe pressure intensifying unit 15 is spaced relationship therewith =to define the chamber B. The chamber B is, in turn, filled with viscous hydraulic fluid 23. Seated within the pressure intensifying unit 16 is the pressure intensifying unit 17 in spaced relationship therewith so as to define the chamber C therebetween. The chamber C is also filled with viscous hydraulic fluid 24.

The chamber D is formed within the pressure intensifying unit 17 and is also filled with viscous hydraulic fluid 25. In a manner hereinafter discussed in detail, the establishment of a relatively low pressure, 30,000 p.s.i., for example, in the chamber A by any well known cylinder 40.

pressure application means such as the pistons 28 (see FIGURE 1), is effective to generate a pressure in the neighborhood of about 1,500,000 p.s.i. in the chamber D. Varying the pressure in the chamber A is eifective to vary the pressure in the chamber D according to a function determined by the relative dimensions of the pressure intensifying units 15, 16, and 17.

Because of the extremely high pressures developed within the intensifying unit 17, the possibility of structural failure of its components is necessarily a factor to be considered. To obviate-the possibility of such failure, fluid under pressure from the chamber C is bled into the intensifying unit 17 to provide lateral support for its components according to the present invention, in a manner hereinafter discussed in detail.

As has previously been pointed out, the ultra-high pressure generating device embodying features of the present invention facilitates heating material placed in the chamber D for compaction, for example, to any predetermined temperature up to 2,000 F., or thereabout. This is significant in powder metallurgy, for example, and is accomplished by electrical resistance through an electrical system 3-0 extending through the multiplying units 15, 16, 17 from a suitable source of power (not shown) externally of the cylinder 20. The same electrical system 30 also readily facilitates testing the electrical conductivity of specimens under varying pressures.

Turning to the details of construction of the pressure generating device 10, the outer cylinder 20 is, in the present instance, a portion of the barrel of a sixteeninch-naval gun. The cylinder 20 is thus fabricated of alloy steel and has an inside diameter at its inner surface of sixteen inches. It will readily sustain internal pressures of far in excess of 30,000 p.s.i., of course.

The pressure intensifying unit is seated within the container on suitably arranged shims or the like (not shown) to support it concentrically within the cylinder 20. Pressure developed in the chamber A by conventional pressure generating devices diagrammatically represented by the pistons 28 (see FIGURE 1) is thus uniformly effective upon the entire pressure intensifying unit 15.

The pressure intensifying unit 15 comprises a cylinder 40 fabricated of alloy steel. In the exemplary unit 15 described here, the outside diameter of the cylinder 40 at its cylindrical outer surface 41 is 15.800 inches so that a 0.100 inch gap remains between the outer surface 41 and the inner surface 33 of the cylinder 20. The cylinder 40 is slipped over and shrunk onto a relatively thick intermediate cylinder 45 also fabricated of alloy steel. The cylinder 45 is, in turn, slipped over and shrunk onto a cylinder 46 fabricated of alloy steel and having an inside diameter at its cylindrical inner surface 47 of 5.610 inches after assembly.

The cylindrical passage through the cylinder 46 defined' by its cylindrical inner surface 47 is closed at opposite ends by a pair of identical primary piston assemblies 50, only One of which is shown in FIGURE 2. Each primary piston assembly 50 comprises a generally circular disc 51 formed of alloy steel and having a planar outer surface 52.

An annular cutout 55 is formed in the periphery of the disc 51 between its cylindrical outer surface 56 and the planar surface 52. Seated in the cut out 55 on its planar base 57 is a sealing ring 58 made of a suitable material such as Fabrica or the like. The diameter of the cylindrical outer surface 60 of this sealing ring 58 is such that an interference fit is established between the surface 60 and the cylindrical inner surface 49 of the Since the sealing ring 58 is compressed tightly against the base 57 of the cut out 55 by an alloy steel retaining plate 65 and a suitable fastener arrangement (not shown) such as bolts or the like, a fluid tight seal is defined between the relatively movable disc 51 and the cylinder 40.

On the side 66 of the sealing ring 58 opposite the pressure chamber A, a frusto-conical surface 67 is formed continuous with the outer cylindrical surface 60. An antiextrusion ring 69 formed of brass and having a generally triangular configuration in cross-section is seated against the frusto-conical surface 67 and serves to prevent extrusion of the Fabrica sealing material between the outer cylindrical surface 56 on the disc 51 and the inner cylindrical surface 49 in the cylinder 40 when the piston assembly 50 is subjected to a relatively high fluid pressure in the chamber A during operation of the ultra-high pressure generating device 10.

The disc 51 is reduced in diameter along a generally frusto-conical inner surface 70 to an inner head 71. The cylindrical outer surface 72 of the head 71 is slightly smaller in diameter than the cylindrical inner surface 47 in the cylinder 46, and, accordingly, fits into the cylinder 46 for sliding movement therein. An air filled chamber 75 is defined between the frusto-conical surface 70 on the disc 51 and the continuous frustoconical ends 76 and 77 of the cylinders 45 and 46, respectively.

Seated against the planar inner face 80 of the head 71 is a sealing ring 81, also formed of Fabrica or the like. The sealing ring 81 has a generally cylindrical outer surface 82, the diameter of which is slightly greater than that of the cylinder surface 47 so that an interference fit is effected between the ring 81 and the cylindrical surface 47. An alloy steel cap 85 secures the ring 81 tightly against the face 80 and is centered relative thereto by complementary projection 86 and depression 87 on the cap 85 and head 71, respectively. The ring 81 thus establishes a fluid tight seal between the cylindrical inner surface 47 in the cylinder 46 and the disc 51 of the primary piston assembly 50.

On the side 89 of the sealing ring 81, opposite the pressure chamber B, a frusto-conical surface 90 is formed continuous with the cylindrical surface 82. An antiextrusion ring 91 identical to the ring 69 hereinbefore discussed, prevents extrusion of the Fa'brica material under the pressures generated in the chamber B. A detailed illustration of the anti-extrusion ring 91 is found in FIGURE 3.

The pressure intensifying unit 16 is concentrically supported within the cylinder 46 on suitably arranged shims. Pressure developed within the chamber B by the piston assemblies 50 is uniformly effective upon the pressure intensifying unit 16. The relative dimensions of the outer faces 52 on the piston assemblies 50 and the heads 71 hereof are such that a 30,000 p.s.i. pressure on the chamber A is multiplied to approximately a 240,000 p.s.i. pressure in chamber B.

The pressure intensifying unit 16 comprises a cylinder fabricated of alloy steel and 5.410 inches in diameter. A cylindrical 0.100 inch gap 101 thus remains between theouter cylindrical surface 102 of the cylinder 100 and the inner cylindrical surface 47 of the cylinder 46. The cylinder 100 is slipped over and shrunk onto a smaller diameter alloy steel cylinder 105 which has an inner lining 106 of ceramic material. The diameter of the cylindrical inner surface 107 on the ceramic material is, in the present instance, 2.610 inches after assembly.

The opposite ends of the passage defined by the cylindrical inner surface 109 in the cylinder 100 are closed by a pair of secondary piston assemblies 110 slidable therein. Each of the secondary piston assemblies 110 includes a cylindrical outer disc 111 and a generally cylindrical inner disc 112 having a Fabrica sealing ring 113 retained therebetween. The discs 111 and 112 have cylindrical peripheral surfaces 115 and 116, respectively, which are slightly smaller in diameter than the cylindrical innersurface 109 of the cylinder 100 and, accordingly, slide freely therein.

' 151 with a diameter of 2.510 inches.

The cylindrical outer surface 118 on the Fabrica sealing ring 113 has a slightly larger diameter than the surface 109, and an interference fit is established between this cylindrical outer surface 118 and the inner surface 109 of the cylinder 100. The sealing ring 113 thus establishes a fluid-tight seal between the secondary piston assemblies 110 and the cylinder 100.

To prevent extrusion of the Fabrica sealing ring 113 under pressure developed in chamber B, a frusto-conical surface 119 is formed adjacent the opposite face 120 of the ring 113 continuous with its peripheral cylindrical surface 118 and a brass anti-extrusion ring 121 is seated thereagainst; the ring 121 is identical to the brass ring 69 hereinbefore discussed and a mirror image of the ring 90.

The alloy steel discs 111 and 112 retain the sealing ring 113 between them and are centered relative to each other through the medium of a cup shaped depression 123 formed on the axis of the disc 111 and a complementary projection 124 formed on the disc 112, as illustrated. The discs 111 and 112 are held together by any conven- I tional means such as bolts or the like (not shown).

An inwardly facing shallow cup-shaped depression 130 is formed in the disc 112 of each piston assembly 110 and is lined with ceramic material 131. Seated against the cup-shaped inner surface 132 of the ceramic material is a solid ceramic disc 134. The solid ceramic disc 134 is gold plated to provide an electrical circuit across the disc 134 for reasons which will hereinafter be discussed.

The diameter of the outer surface 136 on the gold plate 135 is 2.610 inches so that the disc 134 slides in sealing relationship with the cylindrical inner surface 107 of the ceramic lining 106 in the cylinder 105. An air filled chamber 138 is defined between the opposed generally frusto-conical surfaces 139 and 140 on the disc 112 and the cylinder 105, respectively,'and the cylindrical surfaces 136 and 109 of the gold plate 135 and the cylinder 100, respectively. v

It has been pointed out that a pressure of approximately 240,000 p.s.i. is developed in the chamber B, when 30,- 000 p.s.i. is applied in chamber A. By virtue of the di mensional relationship between the alloy steel disc 111 of the piston assembly 110, and the plated ceramic disc 134, this pressure of 240,000 p.s.i. in the chamber B is multiplied to a pressure of about 700,000 p.s.i. in the chamber C. Accordingly, the pressure intensifying unit 17, which is seated within the ceramic lining 106 of the cylinder 105 on suitably arranged shims or the like (not shown), is uniformly subjected to a pressure of about 700,000 p.s.i.

The pressure intensifying unit 17 is, according to the present invention, more sophisticated than the pressure intensifying units 15 and 16 because of the substantially greater pressures to which it is subjected, both internally and externally. The pressure intensifying unit 17 comprises a cylinder 150 having a cylindrical outer surface of 0.050 inch is defined between the surfaces 151 and 107.

The cylinder 150 has an annular relief 155 formed in Accordingly a gap.

the interior of each end, as illustrated, and filled with ceramic material 156. The cylindrical inner surface 157 of the ceramic material 156 and the cylindrical inner surface 158 of the cylinder thus form a co-extensive cylindrical surface.

The cylinder 150 is slipped over and shrunk onto a smaller diameter cylinder 160 fabricated of alloy steel and having cylindrical ceramic sections 161 formed on its opposite ends, as illustrated. The cylindrical inner surfaces 162 on the ceramic sections 161 and the cylindrical inner surface 163 in the alloy steel cylinder 160 are co-extensive to form a continuous cylindrical surface.

The cylinder 160 is, in turn, slipped over and shrunk onto an alloy steel cylinder 165 of still smaller diameter,

by identical piston assemblies 170. Each of the piston assemblies is formed of a ceramic block 171 coated with gold plate 172 to afford electrical conductivity across it, for reasons which will hereinafter be discussed.

The ceramic block 171 is stepped in three cylindrical sections 175, 176, and 177, as illustrated. The outer cylindrical surface 178 of the gold plate 172 on the section has virtually the same diameter as the inner surface 157 on the ceramic sections .156 in the cylinder 150. Accordingly, a fluid tight seal is provided between the section 175 of each piston assembly 170 and the cylinder 150.

In identical fashion, the outer cylindrical surface 179 of the gold plate 172 on the central section 176 has an outside diameter virtually the same as the inside diameter of the inner cylindrical surface 162 on the ceramic insert 161. A fluid tight seal is thus defined between the cylinder 160 and the central section 176 of each piston assembly 170. At the same time, an air filled chamber 180 is defined in annular relationship around the cen- The gold plate 172 on the inner section 177 of each 0 ceramic block 171 has an outside diameter of .900 inch and, accordingly, slides in sealing relationship with the inner surface 167 formed on the ceramic coating 166 of the cylinder 165. A fluid tight seal is established between these surfaces and a chamber 181 defined around the periphery of the inner section 177 between it and the ceramic insert 161 of the cylinder 160, as well as between the center section 176 and the cylinder 165. The ultimate pressure chamber D is, of course, defined between the opposite inner faces 182 of the gold plate 172 on the piston assemblies 170 and the cylindrical inner surface 167 of the ceramic coating 166..

The relative dimensions of the outer faces 183 on the ceramic blocks 171 and the inner faces 181 thereon are such that the 700,000 p.s.i. pressure developed in the chamber C is built up to a pressure of approximately 1,500,000 p.s.i. in the ultimate pressure chamber D. To prevent crushing the ceramic blocks 171 under such tremendous pressure, diamond drilled apertures 185 surrounding the innermost sections 177 of the piston assemblies 170. Accordingly, the pressure developed in the chamber C is transmitted through the apertures 185 into the chambers 181 and supports the piston assemblies 170 laterally at their innermost sections 177 as pressure is developed in the ultimate pressure chamber D.

The material to be compressed or compacted is placed within the chamber D by disassembling the intensifying units 15, 16 and 17 through the medium of removing respective piston assemblies 50, 110, and 170 from one end of the device 10. When these piston assemblies 50, 110, and 170 are reinserted'with the material to be compacted or compressed in the chamber D, fluid pressure is applied in the chamber. 30,000 p.s.i. in the present instance, and a pressure of 1,500,000 p.s.i. is uniformly applied to the material in the chamber D. A predetermined compaction or compression of the material, determined 'by the amount of pressure applied, .is effected without the development of any substantial shear stresses in the material because of the uniformity of application of pressure. In practice, compression of material up to twenty-five percent is readily achieved.

If at the same time, it is desirable to apply heat to the material being compressed in the ultimate pressure chamber D, as in the case in powder metallurgy, for example, the resistance heating system 30 is utilized. The resistance heating system comprises an insulated brass rod(s) (only one shown) 200 extending through the discs 51 and caps 85 of the piston assemblies 50. The rods 200 terminate in brass heads 201 which are insulated from the caps 85 and secured by brazing or the like to plastic covered copper strips 204 in the chamber B.

The plastic covered copper strips 204 are, in turn, brazed to brass heads 206 on insulated brass rods 207 extending through the discs 111 of the piston head as semblies 110 in the pressure intensifying unit 16. Th rods 207 terminate at their inner ends in brass heads 208 which are insulated from the discs 111 and brazed to plastic covered copper strips 210. The plastic covered copper strips 210 are, in turn, brazed to brass heads 211 on insulated brass rods 212 extending through the discs 112 into the ceramic material 131 lining their cup-Shaped inner surfaces 130. The insulated brass rods 212 terminate in conducting connections with the gold plating 135 on the ceramic disc 134.

In the chamber C, plastic covered copper strips 215 are brazed to the gold plate 135 on the discs 134, as illustrated, .at one end, and at the opposite end of the gold plate 172 on the blocks 171 of the piston assemblies 170 in the pressure intensifying unit 17. Thus, a complete electrical circuit is provided through the pressure intensifying units 15, 16, and 17 from a source of electromotive force. An application of a pre-determined amount of current to these conductors is elfective to develop a predetermined amount of heat in the ultimate pressure chamber D for sintering in a powder metallurgy process, for example.

The resistance heating system 30 is also readily used to test the electrical conductivity of material being compressed in the ultimate pressure chamber D, as has been pointed out. By electrically connecting the material to the gold plate 172 onopposite ceramic blocks 171 of the piston assemblies 170, conductivity at any pressure to which the material is subjected can be tested during operation.

In the operation of the ultra-high pressure generating device 110, it is, of course, ultimately important to be 'able to accurately predict the amount of pressure which will actually be developed in the ultimate pressure chamber D when a predetermined pressure is applied in the chamber A. Accordingly, a calibration curve is first developed for the device 10.

A pressure generating device has been described which far exceeds the performance of any known devices of broadly similar nature. The device 10 incorporates features according to the present invention which permit the application of ultra-high pressures with minimal shear stress development. Furthermore the material being subjected to pressure may also readily be subjected to high temperatures and tested for electrical conductivity.

The innermost intensifying units 17 of the device 10 are constructed according to the present invention to readily withstand extremely high pressures without material failure. By bleeding fluid 24- under pressure from the chamber C into the units 17, later support for the piston assemblies 170 is provided and prevents the ceramic material thereof from being crushed.

While the embodiment described herein is at present considered to be preferred, it is understood that various modifications and improvements may be made therein, and it is intended to cover in the appended claims such modifications and improvements as fall within the true spirit and scope of the invention.

What is desired to be claimed and secured by letters Patent of the United States is:

1. A device for generating ultra-high pressures, comprising: a plurality of pressure intensifying units of decreasing size including a relatively largest unit and a relatively smallest unit, each succeeding smaller unit being nested within the next larger unit so as to define a plurality of pressure chambers, a relatively non-compressible fluid in each of said chambers, a predetermined pressure developed by said relatively largest unit in the outermost chamber being multiplied through succeeding smaller chambers to a predetermined greater pressure in the innermost chamber.

2. The device of claim 1 further characterized in that each of said pressure intensifying units comprises cylinder means having oppositely disposed open ends and a piston assembly seated in each of said open ends, the pressure developed in a chamber surrounding each unit causing the piston assembly associated therewith to exert a predetermined increased pressure on the liquid within said unit.

3. The device of claim 2 further characterized in that each piston assembly includes a piston with a relatively large diameter body and a relatively smaller diameter head, corresponding cylinder means having a relatively large diameter cylinder section for receiving said body in fluid tight relationship and a relatively smaller diameter section for receiving said head for sliding movement in fluid tight relationship.

4. A device for generating ultra-high pressure, comprising: a plurality of pressure intensifying units of decreasing size nested one within the other so as to define a plurality of pressure chambers between said units, and a relatively non-compressible liquid in each of said chambers, the innermost of said units including cylinder means having a passage extending therethrough and oppositely disposed piston means slidable in said passage to exert pressure therebetween, and an annular chamber defined circumferentially of said piston means in said cylinder means, said annular chamber being in communication with the pressure chamber surrounding said unit so that fluid under pressure from said pressure chamber provides lateral support for said piston means.

5. A device for generating ultra-high pressures, comprising: a plurality of pressure intensifying units of decreasing size, including a relatively largest unit and a relatively smallest unit, each succeeding smaller unit being nested within the next larger unit so as to define a plurality of pressurechambers including an outer chamber between said relatively largest unit and the next smaller unit and an ultimate pressure chamber within said relatively smallest unit, each of said pressure intensifying units including cylinder means having a passage therethrough, piston means slidable in each passage and forming a corresponding pressure chamber in each of said cylinder means, a relatively non-compressible fluid in each of said chambers, and electrical circuit means extending through said units from the outermost unit to the ultimate chamber whereby said ultimate chamber can be heated by electrical resistance and the conductivity of a material in said ultimate chamber tested under pressure.

6. The ultra high pressure generating device of claim 5 further characterized in that the piston means in said relatively smallest unit includes a block of ceramic material, and gold plating on said block of ceramic material, said gold plating forming a conductor in said electrical circuit means.

7. The ultra-high pressure generating device of claim 5 further characterized in that said electrical circuit means includes flexible strips of electrically conductive material extending between the piston means across corresponding chambers between said pressure intensifying units.

8. The ultra-high pressure generating device of claim 5 further characterized in that said electrical circuit means includes brass rods extending through predetermined piston means in certain of said pressure intensifying units.

9. A device for generating ultra-high pressures in the range of 1,000,000 psi. and above, comprising: outer cylinder means having a first pressure chamber formed therein and including means for developing a predetermined pressure in said first chamber, a plurality of pressure intensifying units of decreasing size, including a relatively largest unit and a relatively smallest unit nested within each other and within said outer cylinder means so as to define a plurality of pressure chambers, including a second pressure chamber between said relatively largest unit and the next smaller unit and an ultimate pressure chamber within said relatively smallest unit, and a relatively non-compressible fluid in each of said chambers, said predetermined pressure develop-ed in said first chamber being multiplied through succeeding smaller chambers to a predetermined greater pressure in said ultimate pressure chamber.

10. The device of claim 1 further characterized in that said relatively non-compressible fluid comprises a liquid of the type used as hydraulic fluid.

References Cited by the Examiner UNITED STATES PATENTS Solberg et a1. Phanstiehl.

Scott.

Bauer.

Gerard et a1.

Levey.

WILLIAM J. STEPHENSON, Primary Examiner. 

1. A DEVICE FOR GENERATING ULTRA-HIGH PRESSURES, COMPRISING: A PLURALITY OF PRESSURE INTENSIFYING UNITS OF DECREASING SIZE INCLUDING A RELATIVELY LARGEST UNIT AND A RELATIVELY SMALLEST UNIT, EACH SUCCEEDING SMALLER UNIT BEING NESTED WITHIN THE NEXT LARGER UNIT SO AS TO DEFINE A PLURALITY OF PRESSURE CHAMBERS, A RELATIVELY NON-COMPRESSIBLE FLUID IN EACH OF SAID CHAMBERS, A PREDETERMINED PRESSURE DEVELOPED BY SAID RELATIVELY LARGEST UNIT IN THE OUTERMOST CHAMBER BEING MULTIPLIED THROUGH SUCCEEDING SMALLER CHAMBERS TO A PREDETERMINED GREATER PRESSURE IN THE INNERMOST CHAMBER. 